CN111936746B - Rotary compressors and refrigeration cycle devices - Google Patents

Abstract

The rotary compressor includes a compression mechanism unit that compresses a refrigerant inside an airtight container, and a motor arranged above the compression mechanism unit. The compression mechanism part has: first to third refrigerant compressing parts arranged at intervals in the axial direction of the airtight container between the first bearing and the second bearing; interposed between the first refrigerant compressing part and the second refrigerant A first intermediate partition plate between the compression parts; a second intermediate partition plate interposed between the second refrigerant compression part and the third refrigerant compression part; and a rotating shaft to which a rotor of the electric motor is fixed. The compression mechanism part is fixed to the airtight container by a pair of fixing parts provided at two places separated in the axial direction of the rotating shaft, and the center of gravity of the structure including the compression mechanism part and the rotor of the motor is located between the pair of fixing parts.

Description

Rotary compressors and refrigeration cycle devices

technical field

Embodiments of the present invention relate to a multi-cylinder rotary compressor and a refrigeration cycle apparatus including the rotary compressor.

Background technique

In recent years, in order to improve the compressibility of the refrigerant, a vertical three-cylinder type rotary compressor having a compression mechanism in which three sets of refrigerant compressing parts are arranged in the axial direction of the rotating shaft has been developed. The rotary shaft used in this type of rotary compressor includes: first to third crankshaft parts that rotate eccentrically in the cylinder chamber of the refrigerant compression part; A pair of intermediate shaft parts between the third crankshaft parts.

Therefore, compared with a 2-cylinder rotary compressor in which two sets of refrigerant compressing parts are arranged in the axial direction of the rotary shaft, the 3-cylinder rotary compressor has a longer overall length of the rotary shaft and a larger height dimension of the compression mechanism part. .

In addition, since the number of refrigerant compressing parts increases compared with a two-cylinder type two-cylinder rotary compressor, it is necessary to increase the output of the electric motor, which inevitably increases the size of the electric motor.

prior art literature

patent documents

Patent Document 1: Japanese Patent No. 4594302

Patent Document 2: Japanese Patent Application Laid-Open No. 6-26478

Contents of the invention

The problem to be solved by the invention

In the 3-cylinder type rotary compressor, the heavy and large electric motor protrudes from the upper side of the compression mechanism part with an increased height dimension, and the total height of the airtight container housing the compression mechanism part and the motor increases . Therefore, the position of the center of gravity of the three-cylinder type rotary compressor is naturally high, and there is a risk of generating large vibrations during operation.

An object of the present invention is to obtain a rotary compressor capable of reducing vibration during operation, having low noise and high reliability.

means to solve the problem

According to an embodiment, the rotary compressor includes: a cylindrical airtight container; a compression mechanism unit for compressing refrigerant in the airtight container; A stator on the inner peripheral surface of the airtight container; and a rotor surrounded by the stator, and drives the compression mechanism inside the airtight container.

The compression mechanism unit includes: a first bearing and a second bearing arranged at a distance in the axial direction of the airtight container; 1st to 3rd refrigerant compression parts arranged; a first intermediate partition plate interposed between the first refrigerant compression part and the second refrigerant compression part; a second intermediate partition plate between the third refrigerant compression unit; and a rotating shaft to which the rotor of the electric motor is fixed.

The rotating shaft has: a first journal supported by the first bearing; a second journal supported by the second bearing; The first to third crankshaft parts that rotate eccentrically in the cylinder chambers of the first to third refrigerant compression parts and are fitted with roller sleeves; the first intermediate shaft located between the first crankshaft part and the second crankshaft part part; and a second intermediate shaft part located between the second crankshaft part and the third crankshaft part.

The compressing mechanism part is fixed to the airtight container by a pair of fixing parts provided at two places separated in the axial direction of the rotating shaft, and the center of gravity of the structure including the compressing mechanism part and the rotor of the electric motor is located in the airtight container. Between a pair of fixed parts.

Description of drawings

FIG. 1 is a circuit diagram schematically showing the configuration of a refrigeration cycle apparatus according to a first embodiment.

Fig. 2 is a cross-sectional view of the three-cylinder rotary compressor according to the first embodiment.

Fig. 3 is a cross-sectional view of the first refrigerant compressing section schematically showing the positional relationship between the vane and the sleeve.

4 is a cross-sectional view of the first refrigerant compression unit showing the relative positional relationship between the roller sleeve and the vanes in the first cylinder chamber when the rotation angle of the first crankshaft portion of the rotary shaft is 0°.

5 is a cross-sectional view of the first refrigerant compression unit showing the relative positional relationship between the roller sleeve and the vanes in the first cylinder chamber when the rotation angle of the first crankshaft portion of the rotary shaft is 270°.

Fig. 6 is a plan view of a second intermediate partition panel.

Fig. 7 is a plan view showing a state where the second intermediate partition plate is divided into a pair of plate elements.

8 is a plan view showing the positional relationship between the second suction port and the second connecting pipe of the second intermediate partition plate.

(A) of FIG. 9 is a side view of the second intermediate partition plate showing a state in which a pair of plate elements are shifted in the thickness direction. (B) of FIG. 9 is a side view of the second intermediate partition plate in a state where the deviation generated between the pair of plate elements has been corrected by the second connection pipe press-fitted into the second suction port. .

FIG. 10 is a characteristic diagram showing the relationship between the load acting on the rotary shaft and the rotation angle of the rotary shaft.

Fig. 11 is a cross-sectional view of a three-cylinder rotary compressor according to a second embodiment.

Fig. 12 is a cross-sectional view of a three-cylinder rotary compressor according to a third embodiment.

Fig. 13 is a cross-sectional view of a three-cylinder rotary compressor according to a fourth embodiment.

14 is a cross-sectional view of a three-cylinder rotary compressor according to a fifth embodiment.

detailed description

[the first embodiment]

Hereinafter, a first embodiment will be described with reference to FIGS. 1 to 10 .

FIG. 1 is, for example, a refrigeration cycle circuit diagram of an air conditioner 1 that is an example of a refrigeration cycle device. The air conditioner 1 includes a rotary compressor 2 , a four-way valve 3 , an outdoor heat exchanger 4 , an expansion device 5 , and an indoor heat exchanger 6 as main elements. The aforementioned plurality of elements constituting the air conditioner 1 are connected via a circulation circuit 7 through which a refrigerant circulates.

Specifically, as shown in FIG. 1 , the discharge side of the rotary compressor 2 is connected to the first port 3 a of the four-way valve 3 . The second port 3 b of the four-way valve 3 is connected to the outdoor heat exchanger 4 . The outdoor heat exchanger 4 is connected to the indoor heat exchanger 6 via the expansion device 5 . The indoor heat exchanger 6 is connected to the third port 3c of the four-way valve 3 . The fourth port 3 d of the four-way valve 3 is connected to the suction side of the rotary compressor 2 via the accumulator 8 .

When the air conditioner 1 is operated in the cooling mode, the four-way valve 3 is switched so that the first port 3a communicates with the second port 3b, and the third port 3c communicates with the fourth port 3d. When the operation of the air conditioner 1 is started in the cooling mode, the high-temperature, high-pressure gas-phase refrigerant compressed by the rotary compressor 2 is directed to the outdoor heat exchanger functioning as a radiator (condenser) through the four-way valve 3 4 guide.

The gas-phase refrigerant guided to the outdoor heat exchanger 4 is condensed by heat exchange with air, and becomes a high-pressure liquid-phase refrigerant. The high-pressure liquid-phase refrigerant is decompressed in the process of passing through the expansion device 5 to become a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the indoor heat exchanger 6 functioning as a heat absorber (evaporator), and exchanges heat with air while passing through the indoor heat exchanger 6 .

As a result, the gas-liquid two-phase refrigerant deprives air of heat and evaporates, turning into a low-temperature, low-pressure gas-phase refrigerant. The air passing through the indoor heat exchanger 6 is cooled by the latent heat of evaporation of the liquid-phase refrigerant, becomes cold air, and is sent to a place where air conditioning (cooling) is to be performed.

The low-temperature and low-pressure gas-phase refrigerant passing through the indoor heat exchanger 6 is guided to the accumulator 8 through the four-way valve 3 . When a liquid-phase refrigerant that has not been completely evaporated is mixed into the refrigerant, it is separated into a liquid-phase refrigerant and a gas-phase refrigerant in the accumulator 8 . The low-temperature, low-pressure gas-phase refrigerant from which the liquid-phase refrigerant has been separated is sucked into the rotary compressor 2 , recompressed by the rotary compressor 2 into a high-temperature, high-pressure gas-phase refrigerant, and discharged toward the circulation circuit 7 .

On the other hand, when the air conditioner 1 is operating in the heating mode, the four-way valve 3 is switched so that the first port 3a communicates with the third port 3c, and the second port 3b communicates with the fourth port 3d. Therefore, the high-temperature, high-pressure gas-phase refrigerant discharged from the rotary compressor 2 is guided to the indoor heat exchanger 6 via the four-way valve 3 , and exchanges heat with air passing through the indoor heat exchanger 6 . That is, the indoor heat exchanger 6 functions as a condenser.

As a result, the gas-phase refrigerant passing through the indoor heat exchanger 6 is condensed by heat exchange with air, and becomes a high-pressure liquid-phase refrigerant. The air passing through the indoor heat exchanger 6 is heated by heat exchange with the gas-phase refrigerant, becomes hot air, and is sent to a place where air conditioning (heating) is to be performed.

The high-temperature liquid-phase refrigerant passing through the indoor heat exchanger 6 is guided toward the expansion device 5 , and is decompressed while passing through the expansion device 5 to become a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 4 functioning as an evaporator, where it evaporates by exchanging heat with air, and becomes a low-temperature, low-pressure gas-phase refrigerant. The low-temperature, low-pressure gas-phase refrigerant passing through the outdoor heat exchanger 4 is sucked into the rotary compressor 2 through the four-way valve 3 and the accumulator 8 .

Next, a specific structure of the rotary compressor 2 used in the air conditioner 1 will be described with reference to FIGS. 2 to 8 . FIG. 2 is a cross-sectional view showing a vertical three-cylinder rotary compressor 2 . As shown in FIG. 2 , the three-cylinder rotary compressor 2 includes an airtight container 10 , a motor 11 , and a compression mechanism unit 12 as main elements.

The airtight container 10 is divided into three elements, for example, a container main body 10a, a bottom member 10b, and a lid member 10c. The container main body 10a has a cylindrical peripheral wall 10d, and stands vertically. The bottom member 10b is welded to the lower end of the container body 10a so as to airtightly close the lower end opening of the container body 10a. The lid member 10c is welded to the upper end of the container main body 10a so as to airtightly close the upper end opening of the container main body 10a.

The discharge pipe 10e is attached to the lid member 10c of the airtight container 10 . The discharge pipe 10 e is connected to the first port 3 a of the four-way valve 3 via the circulation circuit 7 . In addition, lubricating oil for lubricating the compression mechanism unit 12 is stored in the lower portion of the airtight container 10 .

The electric motor 11 is housed in an intermediate portion along the axial direction of the airtight container 10 so as to be located above the oil surface of the lubricating oil. The electric motor 11 is a so-called inner rotor type motor and includes a stator 13 and a rotor 14 . The stator 13 is fixed to the inner surface of the peripheral wall 10d of the container main body 10a. The rotor 14 is coaxially positioned on the central axis of the airtight container 10 and surrounded by the stator 13 .

The compression mechanism unit 12 is accommodated in the lower part of the airtight container 10 so as to be immersed in lubricating oil. The compression mechanism unit 12 includes, as main elements, a first refrigerant compression unit 15A, a second refrigerant compression unit 15B, a third refrigerant compression unit 15C, a first intermediate partition plate 16, a second intermediate partition plate 17, a first Bearing 18 , second bearing 19 , and rotating shaft 20 .

The first to third refrigerant compression units 15A, 15B, and 15C are arranged in a row at intervals in the axial direction of the airtight container 10 . The first to third refrigerant compression units 15A, 15B, and 15C each have a first cylinder 21a, a second cylinder 21b, and a third cylinder 21c. The thicknesses of the first to third cylinders 21a, 21b, and 21c along the axial direction of the airtight container 10 are set to have the same thickness, for example.

The first intermediate partition plate 16 is interposed between the first cylinder 21a and the second cylinder 21b. The upper surface of the first intermediate partition plate 16 overlaps the lower surface of the first cylinder block 21a so as to cover the inner diameter portion of the first cylinder block 21a from below. The lower surface of the first intermediate partition plate 16 overlaps the upper surface of the second cylinder 21b so as to cover the inner diameter portion of the second cylinder 21b from above.

In addition, a through-hole 16 a is formed in the central portion of the first intermediate partition plate 16 . The through-hole 16a is located between the inner diameter part of the 1st cylinder 21a and the inner diameter part of the 2nd cylinder 21b.

The second intermediate partition plate 17 is interposed between the second cylinder 21b and the third cylinder 21c. The upper surface of the second intermediate partition plate 17 overlaps the lower surface of the second cylinder 21b so as to cover the inner diameter portion of the second cylinder 21b from below. The lower surface of the second intermediate partition plate 17 overlaps the upper surface of the third cylinder 21c so as to cover the inner diameter portion of the third cylinder 21c from above.

In addition, a circular bearing hole 22 is formed in the center portion of the second intermediate partition plate 17 . The bearing hole 22 is located between the inner diameter part of the 2nd cylinder 21b and the inner diameter part of the 3rd cylinder 21c.

The first intermediate partition plate 16 and the second intermediate partition plate 17 have thicknesses T1 and T2 along the axial direction of the airtight container 10 , respectively. According to this embodiment, the thickness T2 of the second intermediate partition plate 17 is thicker than the thickness T1 of the first intermediate partition plate 16 .

As shown in FIG. 2, the 1st bearing 18 is located on the 1st cylinder 21a. The first bearing 18 has a flange portion 23 protruding toward the peripheral wall 10d of the container main body 10a. The flange part 23 overlaps the upper surface of the 1st cylinder 21a so that it may cover the inner diameter part of the 1st cylinder 21a from above.

The flange portion 23 of the first bearing 18, the first cylinder block 21a, the first intermediate partition plate 16, the second cylinder block 21b, and the second intermediate partition plate 17 are stacked in the axial direction of the airtight container 10, and through a plurality of The first fastening bolts 24 (only one is shown in the figure) are integrated together.

A first cylinder chamber 25 is defined by an area surrounded by the inner diameter portion of the first cylinder block 21 a , the first intermediate partition plate 16 , and the flange portion 23 of the first bearing 18 . A second cylinder chamber 26 is defined by an area surrounded by the inner diameter portion of the second cylinder block 21 b , the first intermediate partition plate 16 , and the second intermediate partition plate 17 .

The second bearing 19 is located under the third cylinder 21c. The second bearing 19 has a flange portion 27 protruding toward the peripheral wall 10d of the container main body 10a. The flange part 27 overlaps the lower surface of the 3rd cylinder 21c so that it may cover the inner diameter part of the 3rd cylinder 21c from below.

The flange portion 27 of the second bearing 19, the third cylinder block 21c, and the second intermediate partition plate 17 are stacked in the axial direction of the airtight container 10, and are secured via a plurality of second fastening bolts 28 (only one is shown). combined into one. A region surrounded by the inner diameter portion of the third cylinder block 21 c, the second intermediate partition plate 17 , and the flange portion 27 of the second bearing 19 defines a third cylinder chamber 29 .

Therefore, the first bearing 18 and the second bearing 19 are separated in the axial direction of the airtight container 10, and between the first bearing 18 and the second bearing 19, the first to third cylinders 21a, 21b, 21c are alternately positioned. , the first intermediate partition plate 16 and the second intermediate partition plate 17 .

According to the present embodiment, the flange portion 23 of the first bearing 18 is surrounded by the annular first support member 31 . The first support member 31 has the same thickness as the flange portion 23 of the first bearing 18 . The lower surface of the first support member 31 overlaps the upper surface of the outer peripheral portion of the first cylinder 21 a closest to the motor 11 . The first support member 31 is firmly connected to the outer peripheral portion of the first cylinder 21a via a plurality of third fastening bolts 32 (only one is shown in the drawing).

Moreover, the outer peripheral part of the 1st support member 31 is extended toward the upper direction of the container main body 10a in order to ensure the contact area with the inner surface of the peripheral wall 10d of the container main body 10a. The outer peripheral part of the 1st support member 31 is fixed to the predetermined position of the container main body 10a by methods, such as welding. Therefore, the first support member 31 welded to the container main body 10 a constitutes a first fixing portion 33 that fixes the upper end portion of the compression mechanism portion 12 to the airtight container 10 .

As shown in FIG. 2 , the outer peripheral portion of the third cylinder 21 c protrudes outward in the radial direction of the airtight container 10 from the flange portion 27 of the second bearing 19 . The annular second support member 34 is attached to the lower surface of the outer peripheral portion of the third cylinder 21 c farthest from the motor 11 . The second support member 34 includes: a flat ring portion 35 which receives the lower surface of the outer peripheral portion of the third cylinder 21c; and a cylindrical fitting portion 36 folded downward from the outer peripheral edge of the ring portion 35 .

The ring portion 35 is coupled to the lower surface of the outer peripheral portion of the third cylinder 21c via a plurality of fourth fastening bolts 37 . The fitting portion 36 is fitted inside the peripheral wall 10d of the container body 10a, and the fitting portion 36 is fixed at a predetermined position of the container body 10a by welding or the like.

Therefore, the second support member 34 welded to the container main body 10 a constitutes a second fixing portion 38 that fixes the lower end portion of the compression mechanism portion 12 to the airtight container 10 . The second fixing portion 38 is separated from the first fixing portion 33 by a distance H in the axial direction of the airtight container 10 .

The first discharge muffler 40 is attached to the first bearing 18 . A first muffler chamber 41 is formed between the first discharge muffler 40 and the first bearing 18 . The first muffler chamber 41 opens into the airtight container 10 through an exhaust hole (not shown) included in the first discharge muffler 40 .

The second discharge muffler 42 is attached to the second bearing 19 . A second muffler chamber 43 is formed between the second discharge muffler 42 and the second bearing 19 . The second muffler chamber 43 communicates with the first muffler chamber 41 through a discharge passage (not shown) extending in the axial direction of the airtight container 10 .

As shown in FIG. 2 , the rotating shaft 20 is coaxially positioned on the central axis of the airtight container 10 . The rotary shaft 20 is an integral structure including a first journal portion 45 , a second journal portion 46 , first to third crankshaft portions 47 a , 47 b , and 47 c , a first intermediate shaft portion 48 , and a second intermediate shaft portion 49 .

The first journal portion 45 is located at an intermediate portion along the axial direction of the rotary shaft 20 and is rotatably supported by the first bearing 18 . The rotor 14 of the electric motor 11 is fixed to the upper end portion of the rotating shaft 20 protruding from the first bearing 18 .

The second journal portion 46 is provided coaxially with the first journal portion 45 so as to be located at the lower end portion of the rotary shaft 20 . The second journal portion 46 is rotatably supported by the second bearing 19 .

The first to third crank parts 47 a , 47 b , and 47 c are located between the first journal portion 45 and the second journal portion 46 , and are arranged at intervals in the axial direction of the rotary shaft 20 . The first to third crankshaft portions 47a, 47b, and 47c are disc-shaped elements each having a circular cross-sectional shape, and in this embodiment, the thickness dimension and diameter along the axial direction of the rotating shaft 20 are set to be the same.

The first to third crank parts 47 a , 47 b , 47 c are eccentric with respect to the rotation center line O1 of the rotation shaft 20 , and the eccentric directions are sequentially shifted by 120° in the circumferential direction of the rotation shaft 20 . The first crank portion 47 a is located in the first cylinder chamber 25 . The second crank portion 47 b is located in the second cylinder chamber 26 . The third crank portion 47c is located in the third cylinder chamber 29 .

The first intermediate shaft portion 48 is located between the first crank portion 47 a and the second crank portion 47 b on the rotational center line O1 of the rotary shaft 20 , and penetrates through the through hole 16 a of the first intermediate partition plate 16 .

The second intermediate shaft portion 49 is located between the second crankshaft portion 47b and the third crankshaft portion 47c on the rotation center line O1 of the rotary shaft 20, and is fitted in the second intermediate partition so as to be slidable in the direction around the axis. Bearing hole 22 of plate 17. Through this fitting, the second intermediate partition plate 17 also functions as a third bearing that supports the rotary shaft 20 between the first bearing 18 and the second bearing 19 .

The ring-shaped sleeve 51 is fitted on the outer peripheral surface of the first crank portion 47a. The roller sleeve 51 rotates eccentrically in the first cylinder chamber 25 following the rotating shaft 20 , and a part of the outer peripheral surface of the roller sleeve 51 is in linear contact with the inner peripheral surface of the inner diameter portion of the first cylinder 21 a in a slidable manner.

The upper end surface of the roller sleeve 51 is in slidable contact with the lower surface of the flange portion 23 of the first bearing 18 . The lower end surface of the roller sleeve 51 is in slidable contact with the upper surface of the first intermediate partition plate 16 . Accordingly, the airtightness of the first cylinder chamber 25 can be ensured.

The ring-shaped sleeve 52 is fitted on the outer peripheral surface of the second crank portion 47b. The roller sleeve 52 rotates eccentrically in the second cylinder chamber 26 following the rotating shaft 20 , and a part of the outer peripheral surface of the roller sleeve 52 is in linear contact with the inner peripheral surface of the inner diameter portion of the second cylinder 21 b in a slidable manner.

The upper end surface of the roller sleeve 52 is in slidable contact with the lower surface of the first intermediate partition plate 16 . The lower end surface of the roller sleeve 52 is in slidable contact with the upper surface of the second intermediate partition plate 17 . Thereby, the airtightness of the second cylinder chamber 26 can be ensured.

The ring-shaped sleeve 53 is fitted on the outer peripheral surface of the third crank portion 47c. The roller sleeve 53 rotates eccentrically in the third cylinder chamber 29 following the rotating shaft 20 , and a part of the outer peripheral surface of the roller sleeve 53 is in linear contact with the inner peripheral surface of the inner diameter portion of the third cylinder 21 c in a slidable manner.

The upper end surface of the roller sleeve 53 is in slidable contact with the lower surface of the second intermediate partition plate 17 . The lower end surface of the roller sleeve 53 is in slidable contact with the upper surface of the flange portion 27 of the second bearing 19 . Thereby, the airtightness of the third cylinder chamber 29 can be ensured.

As represented by the first cylinder 21a in FIGS. 3 to 5 , vane slits 55 are formed in the first to third cylinders 21a, 21b, and 21c, respectively. The vane slit 55 extends in the radial direction of the first cylinder chamber 25 .

The vane 56 is housed in the vane slit 55 . The vane 56 is movable in the radial direction of the first cylinder chamber 25 along the vane slit 55 and is urged toward the first cylinder chamber 25 via a spring 57 . The front end portion of the vane 56 is slidably pressed against the outer peripheral surface of the sleeve 51 .

The vane 56 cooperates with the sleeve 51 to divide the first cylinder chamber 25 into a suction region R1 and a compression region R2. In addition, the blade 56 can reciprocate between the protruding position P1 and the sinking position P2 following the eccentric rotation of the sleeve 51 .

FIG. 3 discloses a state where the blade 56 is moved to the projected position P1. At the protruding position P1, the vane 56 protrudes to the inside of the first cylinder chamber 25 to the maximum. At the sinking position P2, the vane 56 is pushed into the vane slit 55 so as to withdraw from the first cylinder chamber 25 . As a result, when the roller sleeve 51 rotates eccentrically, the volumes of the suction region R1 and the compression region R2 of the first cylinder chamber 25 change continuously.

Although not shown, the second cylinder chamber 26 and the third cylinder chamber 29 are also divided into a suction region and a compression region by similar vanes. Therefore, when the roller sleeves 52 and 53 rotate eccentrically, the volumes of the suction region and the compression region of the second cylinder chamber 26 and the third cylinder chamber 29 change continuously.

As shown in FIG. 2 , the first cylinder chamber 25 is connected to the accumulator 8 through a first suction pipe 60 . The second cylinder chamber 26 and the third cylinder chamber 29 are connected to the accumulator 8 via the second intermediate partition plate 17 and the second suction pipe 61 .

Specifically, as shown in FIG. 3 , a first suction port 62 connected to the suction region R1 of the first cylinder chamber 25 is formed inside the first cylinder 21 a. The first suction port 62 opens on the outer surface of the first cylinder block 21 a and extends from the opening end toward the center of the first cylinder chamber 25 .

Moreover, the 1st connection pipe 63 is press-fitted from the outer side of the 1st cylinder 21a into the 1st suction port 62. As shown in FIG. The first connecting pipe 63 protrudes to the outside of the airtight container 10 through the peripheral wall 10d of the container main body 10a, and the downstream end of the first suction pipe 60 is inserted into the inside of the first connecting pipe 63 in an airtight manner.

As shown in FIG. 6 , a joint portion 65 is formed on a part of the outer peripheral portion of the second intermediate partition plate 17 . The joint portion 65 protrudes from the outer peripheral portion of the second intermediate partition plate 17 toward the peripheral wall 10d of the container main body 10a. The second suction port 66 and two branch passages 67a and 67b bifurcated from the downstream end of the second suction port 66 are formed inside the joint part 65 .

The second suction port 66 opens at the protruding end of the joint portion 65 and extends from the protruding end toward the center portion of the second intermediate partition plate 17 . In addition, the second connection pipe 68 is pressed into the second suction port 66 from the outside of the second intermediate partition plate 17 . The second connecting pipe 68 protrudes to the outside of the airtight container 10 through the peripheral wall 10d of the container main body 10a, and the downstream end of the second suction pipe 61 is inserted into the second connecting pipe 68 in an airtight manner.

One branch passage 67 a is opened on the upper surface of the second intermediate partition plate 17 so as to communicate with the second cylinder chamber 26 . The other branch passage 67b opens to the lower surface of the second intermediate partition plate 17 so as to communicate with the third cylinder chamber 29 .

As shown in FIG. 2 , the flange portion 23 of the first bearing 18 is provided with a first discharge valve 70 that opens when the pressure in the compression region R2 of the first cylinder chamber 25 reaches a predetermined value. The discharge side of the first discharge valve 70 communicates with the first muffler chamber 41 .

The first intermediate partition plate 16 is provided with a second discharge valve 71 that opens when the pressure in the compression region R2 of the second cylinder chamber 26 reaches a predetermined value. The discharge side of the second discharge valve 71 communicates with the first muffler chamber 41 via a discharge passage (not shown) provided inside the first intermediate partition plate 16 and inside the first cylinder 21 a.

A third discharge valve 72 that opens when the pressure in the compression region R2 of the third cylinder chamber 29 reaches a predetermined value is provided on the flange portion 27 of the second bearing 19 . The discharge side of the third discharge valve 72 communicates with the second muffler chamber 43 .

In such a 3-cylinder type rotary compressor 2, when the rotating shaft 20 is rotated by the motor 11, the roller sleeves 51, 52, 53 follow the first to third crankshaft portions 47a, 47b, 47c and rotate between the first to the third crankshafts. Eccentric rotation in 3 cylinder chambers 25,26,29. As a result, the volumes of the suction region R1 and the compression region R2 of the first to third cylinder chambers 25 , 26 , and 29 change, and the gas-phase refrigerant in the accumulator 8 is sucked through the first suction pipe 60 and the second suction pipe 61 . To the suction region R1 of the first to third cylinder chambers 25 , 26 , 29 .

The gas-phase refrigerant sucked into the suction region R1 of the first cylinder chamber 25 through the first suction port 62 from the first suction pipe 60 is gradually compressed during the transition from the suction region R1 to the compression region R2. When the pressure of the gas-phase refrigerant reaches a predetermined value, the first discharge valve 70 opens, and the gas-phase refrigerant compressed in the first cylinder chamber 25 is discharged to the first muffler chamber 41 .

Part of the gas-phase refrigerant introduced from the second suction pipe 61 to the second suction port 66 of the second intermediate partition plate 17 is sucked into the suction region R1 of the second cylinder chamber 26 through one branch passage 67 a. The gas-phase refrigerant sucked into the suction region R1 of the second cylinder chamber 26 is gradually compressed during the transition from the suction region R1 to the compression region R2. When the pressure of the gas-phase refrigerant reaches a predetermined value, the second discharge valve 71 opens, and the gas-phase refrigerant compressed in the second cylinder chamber 26 is guided to the first muffler chamber 41 through the discharge passage.

The remaining gas-phase refrigerant guided from the second suction pipe 61 to the second suction port 66 of the second intermediate partition plate 17 is sucked into the suction region R1 of the third cylinder chamber 29 through the other branch passage 67b. The gas-phase refrigerant sucked into the suction region R1 of the third cylinder chamber 29 is gradually compressed during the transition from the suction region R1 to the compression region R2. When the pressure of the gas-phase refrigerant reaches a predetermined value, the third discharge valve 72 opens, and the gas-phase refrigerant compressed in the third cylinder chamber 29 is discharged to the second muffler chamber 43 . The gas-phase refrigerant discharged into the second muffling chamber 43 is guided to the first muffling chamber 41 through the discharge passage.

The eccentric directions of the first to third crank parts 47 a , 47 b , 47 c of the rotary shaft 20 are sequentially shifted by 120° in the circumferential direction of the rotary shaft 20 . Therefore, there is an equal phase difference in the timing at which the gas-phase refrigerant compressed in the first to third cylinder chambers 25 , 26 , and 29 is discharged.

The gas-phase refrigerant compressed in the first to third cylinder chambers 25 , 26 , and 29 joins in the first muffler chamber 41 and is continuously discharged from the exhaust hole of the first discharge muffler 40 toward the inside of the airtight container 10 . discharge. The gas-phase refrigerant discharged into the airtight container 10 is guided from the discharge pipe 10 e to the four-way valve 3 after passing through the motor 11 .

In the three-cylinder rotary compressor 2 of the present embodiment, the upper end portion of the compression mechanism portion 12 having the first to third refrigerant compression portions 15A, 15B, and 15C is fixed to the airtight container 10 by the first fixing portion 33 to compress The lower end of the mechanism part 12 is fixed to the airtight container 10 by the second fixing part 38 .

That is, the compression mechanism part 12 is fixed to the airtight container 10 at two locations separated in the axial direction of the rotating shaft 20 , and the first fixing part 33 and the second fixing part 38 are separated by a distance H in the axial direction of the rotating shaft 20 .

In addition, in this embodiment, for example, by optimizing the weight distribution of various components constituting the compression mechanism unit 12, the center of gravity G of the structure including the rotor 14 of the motor 11 and the compression mechanism unit 12 is positioned at the first fixed position. Part 33 and the second fixing part 38 within the range of the distance H. Specifically, the center of gravity G is located on the axis of the first intermediate shaft portion 48 spanning between the first crankshaft portion 47a and the second crankshaft portion 47b as shown in FIG. 2 .

On the other hand, in the three-cylinder type rotary compressor 2 of this embodiment, the suction region R1 of the second cylinder chamber 26 and the third cylinder chamber 29 passes through the second suction port 66 provided in the second intermediate partition plate 17 and the suction region R1. The accumulator 8 is connected to the branch passages 67a and 67b.

Therefore, it is unavoidable that the refrigerant suction path of the second cylinder chamber 26 and the third cylinder chamber 29 is longer than the refrigerant suction path of the first cylinder chamber 25 . Therefore, in order to make the pressure loss generated when the second cylinder chamber 26 and the third cylinder chamber 29 are in the suction stroke equal to the pressure loss generated in the first cylinder chamber 25 , it is necessary to increase the volume of the refrigerant suction path in short.

As a result, the thickness T2 of the second intermediate partition plate 17 having the second suction port 66 and the branch passages 67a, 67b increases, and accordingly, the second intermediate shaft between the second crankshaft portion 47b and the third crankshaft portion 47c The full length of part 49 becomes long.

Therefore, in the present embodiment, in order to suppress the deflection of the rotating shaft 20, the bearing hole 22 for supporting the second intermediate shaft portion 49 in a rotatable manner is formed in the second intermediate partition plate 17, and the second intermediate partition plate 17 also serves as the second intermediate partition plate 17. It functions as a third bearing that supports the rotating shaft 20 .

In this case, since the rotary shaft 20 is an integral structure, unless the second intermediate partition plate 17 is divided, the second intermediate shaft portion 49 of the rotary shaft 20 and the second intermediate partition plate 17 cannot be separated. The bearing hole 22 is fitted.

Therefore, in this embodiment, as shown in FIGS. 6 to 8 , the second intermediate partition plate 17 is divided into a first plate element 75 a and a second plate element 75 b along the radial direction of the second intermediate shaft portion 49 . The first plate element 75a and the second plate element 75b have vertical joint surfaces 76a, 76b along the axial direction of the second intermediate shaft portion 49, respectively. The joining surfaces 76a and 76b are butted against each other, and define a dividing line X forming a straight line. The dividing line X extends, for example, in the radial direction of the second intermediate partition plate 17 so as to connect the center of the second suction port 66 and the center of the bearing hole 22 .

As shown in FIG. 7, the 1st recessed part 77a, 77b curved in an arc shape is formed in the 1st plate element 75a and the 2nd plate element 75b, respectively. The first recesses 77a, 77b define the bearing hole 22 in cooperation with each other when the joint surface 76a of the first plate element 75a and the joint surface 76b of the second plate element 75b are brought into contact with each other.

Therefore, when the joint surface 76a of the first plate element 75a is brought into contact with the joint surface 76b of the second plate element 75b, the second intermediate shaft portion 49 of the rotary shaft 20 is sandwiched from the radial direction by the first recesses 77a, 77b, As a result, the second intermediate shaft portion 49 is slidably fitted to the bearing hole 22 .

Moreover, the 2nd recessed part 78a, 78b curved in arc shape is formed in the edge part of the joint surface 76a, 76b of the 1st plate element 75a and the 2nd plate element 75b, respectively. The second recesses 78a, 78b define the second suction port 66 in cooperation with each other when the joint surface 76a of the first plate element 75a and the joint surface 76b of the second plate element 75b are brought into contact with each other. Therefore, the 2nd connection pipe 68 is press-fitted across between the 2nd recessed part 78a, 78b, and the outer peripheral surface of the 2nd connection pipe 68 contacts the inner peripheral surface of the 2nd recessed part 78a, 78b.

In addition, the branch passages 67a and 67b of the second intermediate partition plate 17 are located on the dividing line X, and part of the second recesses 78a and 78b constitute the branch passages 67a and 67b.

In the three-cylinder rotary compressor 2 , when the gas-phase refrigerant is compressed in the first to third cylinder chambers 25 , 26 , and 29 , a load tending to press the rotary shaft 20 in the radial direction occurs. The blank arrow Y shown in FIG. 3 indicates the direction of the load received by the rotating shaft 20 due to the load when the roller sleeve 51 compresses the gas-phase refrigerant in the first cylinder chamber 25 .

In the compression process in which the gas-phase refrigerant is compressed, the load applied to the rotating shaft 20 changes according to the rotation angle of the rotating shaft 20, and the inner peripheral surface of the bearing hole 22 of the second intermediate partition plate 17 supporting the rotating shaft 20 The received load also differs depending on the position of the bearing hole 22 in the circumferential direction.

10 shows, for example, the relationship between the rotation angle of the second crankshaft portion 47b located above the second intermediate partition plate 17 and the load acting on the rotating shaft 20, and the relationship between the bearing holes 22 when a load acts on the rotating shaft 20. The direction of the load on the inner peripheral surface. The load acting on the rotary shaft 20 is the sum of the forces pressing the first to third crank parts 47 a , 47 b , 47 c via the roller sleeves 51 , 52 , 53 .

In addition, the rotation angle of the rotary shaft 20 refers to a position where the eccentric direction of the second crankshaft portion 47b is in the direction of the vane 56 and the vane 56 is pushed into the vane slit 55 to the maximum extent as a reference (0°). The angle of the rotation direction of the rotation shaft 20 .

As shown in FIG. 10 , the load acting on the rotating shaft 20 reaches a peak when the rotation angle of the second crankshaft portion 47 b is approximately in the range of 120° to 250°, and drops sharply when the rotation angle exceeds 250°.

According to the present embodiment, the load acting on the rotating shaft 20 reaches 85% of the peak value when the rotation angle of the second crank portion 47b is in the range of approximately 110° to 280°. When the rotation angle of the second crankshaft portion 47b is approximately 110°, the bearing hole 22 of the second intermediate partition plate 17 is viewed from the axial direction of the rotation shaft 20, with the direction of the vane 56 as a reference position, and the direction of the blade 56 is used as a reference position. There is a load acting in a direction of rotation of 50°.

In addition, when the rotation angle of the second crank portion 47 b is approximately 280°, a load acts in the direction of 150° on the bearing hole 22 of the second intermediate partition plate 17 .

FIG. 6 shows the positional relationship between the dividing line X of the second intermediate partition plate 17 divided into two and the blades 56 . As can be seen from FIG. 6 , regarding the dividing line X of the second intermediate partition plate 17 , viewed from the axial direction of the rotating shaft 20 , the direction of the vane 56 is used as a reference position, and it is set at a distance of 50° to 50° in the rotating direction of the rotating shaft 20 . 150° for the location of the region θ.

Therefore, the joining surfaces 76a, 76b of the first plate element 75a and the second plate element 75b defining the dividing line X are provided at positions where the load acting on the bearing hole 22 from the rotating shaft 20 is 85% or less of the peak value.

According to the first embodiment, the center of gravity G of the structure including the rotor 14 of the electric motor 11 and the compression mechanism part 12 is located just across the first crankshaft part within the range of the distance H between the first fixing part 33 and the second fixing part 38 47a and the second crankshaft portion 47b on the axis of the first intermediate shaft portion 48.

According to this configuration, when the gas-phase refrigerant is compressed, although pressure fluctuations occur at the three locations of the first to third cylinder chambers 25, 26, and 29, it is possible to avoid the distance from the three locations where the pressure fluctuations occur to the center of gravity G. The distance produces a large deviation. Therefore, the compression mechanism part 12 which is a vibration source can be firmly supported by the airtight container 10, and the vibration of the compression mechanism part 12 can be suppressed.

Therefore, it is possible to provide the highly reliable three-cylinder rotary compressor 2 that suppresses vibrations that cause noise and various failures.

In addition, in the first embodiment, the second intermediate partition plate 17 also functions as a third bearing that rotatably supports the second intermediate shaft portion 49 of the rotary shaft 20 . Therefore, it is possible to suppress deflection and shaft vibration of the rotary shaft 20 during operation of the three-cylinder rotary compressor 2 , and also contribute to reduction of vibration and noise of the three-cylinder rotary compressor 2 in this regard.

In addition, the dividing line X passing through the joining surfaces 76a, 76b of the second intermediate partition plate 17 is set in the direction of rotation of the rotating shaft 20 with the direction of the blade 56 as a reference position (reference point) as viewed from the axial direction of the rotating shaft 20 . Avoid the position of θ in the area of 50°～150°.

Slight steps or the like are likely to occur at the junction of the bearing holes 22 formed by the first recesses 77a and 77b, but by adopting the above-mentioned structure, the second intermediate partition plate 17 is divided into the first plate element 75a and the second plate element 75a. These two parts of the element 75b can also prevent a large load from acting on the joint portion of the bearing hole 22 . Therefore, abrasion of the bearing hole 22 and the second intermediate shaft portion 49 can be prevented.

In addition, since the second suction port 66 is located on the dividing line X, the second recesses 78a, 78b formed on the joint surfaces 76a, 76b of the first plate element 75a and the second plate element 75b are formed on the joint surfaces 76a, 76b. When 76b is docked, the two cooperate with each other to define the second suction port 66 .

In this case, as indicated by blank arrows in FIG. 9(A), the bolt fastening force is applied to the second intermediate partition plate 17 from the second cylinder block 21b and the third cylinder block 21c side. At this time, for example, if the tightening force of the bolts varies, as shown in (A) of FIG. 2. A slight step S is formed on the upper surface and the lower surface of the intermediate partition plate 17.

The upper surface and the lower surface of the second intermediate partition plate 17 are sliding surfaces for the roller sleeves 52 and 53 to slidably contact. This is one of the causes of wear and decrease in the airtightness of the second cylinder chamber 26 and the third cylinder chamber 29 .

In this embodiment, in the state where the second intermediate partition plate 17 is interposed between the second cylinder block 21b and the third cylinder block 21c, the second suction pipe 68 is pressed from the outside of the second intermediate partition plate 17 . into the second suction port 66 defined by the second recesses 78a, 78b.

By this press-fitting, the slight deviation generated between the first plate element 75a and the second plate element 75b is corrected, and as shown in FIG. 9(B), the upper surface and the lower surface of the second intermediate partition plate 17 The surface becomes a flat surface with no level difference.

Therefore, wear of the roller sleeves 52 and 53 can be avoided, and the airtightness of the second cylinder chamber 26 and the third cylinder chamber 29 can be improved, so that leakage of the gas-phase refrigerant can be prevented.

The position of the dividing line X which divides the second intermediate partition plate 17 is not specified in the first embodiment. For example, as shown by a reference sign Z in FIG. 6, the dividing line may also be set at a position connecting the reference point B corresponding to the blade 56 and the center of the bearing hole 22. Regarding the position of the dividing line, as long as it is within the axis of rotation, It is only necessary for the rotation direction of 20 to deviate from the region θ of 50° to 150°, and there is no special restriction.

In addition, in the above-mentioned first embodiment, by forming the second intermediate partition plate 17 into two parts, the second intermediate partition plate 17 also serves as the second intermediate shaft for the counter rotating shaft 20 . The function of the third bearing that supports the portion 49 is not limited thereto.

For example, instead of the second intermediate partition plate 17, the first intermediate partition plate 16 can also be formed into a structure divided into two parts, so that the first intermediate partition plate 16 can also serve as a support for the rotating shaft 20. The function of the third bearing supported by the first intermediate shaft portion 48 .

[the second embodiment]

Fig. 11 discloses a second embodiment. The structure of fixing the lower end part of the compression mechanism part 12 to the airtight container 10 of 2nd Embodiment differs from 1st Embodiment. Other than that, the configuration of the three-cylinder rotary compressor 2 is the same as that of the first embodiment. Therefore, in the second embodiment, the same reference numerals are assigned to the same components as those in the first embodiment, and description thereof will be omitted.

As shown in FIG. 11, the 2nd support member 80 which comprises the 2nd fixing part 38 is interposed between the flange part 27 of the 2nd bearing 19, and the container main body 10a. The second support member 80 includes: a ring portion 81 surrounding the flange portion 27; a cylindrical inner peripheral wall portion 82 standing from the inner peripheral edge of the ring portion 81; The outer peripheral wall portion 83.

The inner peripheral wall portion 82 of the second support member 80 is press-fitted into the outer peripheral surface of the flange portion 27 of the second bearing 19 from below the compression mechanism portion 12 prior to the outer peripheral wall portion 83 . The outer peripheral wall portion 83 of the second support member 80 is pressed into the container body 10a from the lower end opening of the container body 10a before the bottom member 10b closes the lower end opening of the container body 10a.

Also in such a structure, the lower end portion of the compression mechanism portion 12 having the first to third refrigerant compression portions 15A, 15B, and 15C is fixed to the airtight container 10 at the second fixing portion 38 , and the rotor of the motor 11 is included. 14 and the center of gravity G of the structure of the compression mechanism part 12 is located within the range of the distance H between the first fixing part 33 and the second fixing part 38 .

[the third embodiment]

A third embodiment is disclosed in FIG. 12 . The matters related to the shape of the second support member 80 in the third embodiment are different from those in the second embodiment.

As shown in FIG. 12 , the second support member 80 according to the third embodiment includes: a ring portion 84 surrounding the flange portion 27; a cylindrical inner peripheral wall portion 85 folded downward from the inner peripheral edge of the ring portion 84; A cylindrical outer peripheral wall portion 86 folded back downward from the outer peripheral edge of the ring portion 84 ; and an annular flange portion 87 folded back inward from the lower end of the outer peripheral wall portion 86 .

The inner peripheral wall portion 85 of the second support member 80 is press-fitted into the outer peripheral surface of the flange portion 27 of the second bearing 19 from below the compression mechanism portion 12 prior to the outer peripheral wall portion 86 . The outer peripheral wall portion 86 of the second supporting member 80 is pressed into the inside of the container body 10a from the lower end opening of the container body 10a before the bottom member 10b closes the lower end opening of the container body 10a. The flange portion 87 abuts against the upper end portion of the bottom member 10b when the lower end opening of the container main body 10a is closed by the bottom member 10b.

[the fourth embodiment]

A fourth embodiment is disclosed in FIG. 13 . The structure of fixing the lower end part of the compression mechanism part 12 to the airtight container 10 of 4th Embodiment differs from 1st Embodiment. Other than that, the configuration of the three-cylinder rotary compressor 2 is the same as that of the first embodiment. Therefore, in the second embodiment, the same reference numerals are assigned to the same components as those in the first embodiment, and description thereof will be omitted.

As shown in FIG. 13, the 3rd cylinder 21c has the outer peripheral surface formed so that it may follow the inner peripheral surface of the container main body 10a. The third cylinder 21c is fitted inside the container main body 10a, and its outer peripheral surface is directly fixed to a predetermined position of the container main body 10a by welding or the like.

Therefore, in the fourth embodiment, the welding portion 90 formed between the third cylinder 21c and the container main body 10a constitutes the second fixing portion 38 for fixing the lower end portion of the compression mechanism portion 12 to the airtight container 10 .

Also in such a structure, the lower end portion of the compression mechanism portion 12 having the first to third refrigerant compression portions 15A, 15B, and 15C is fixed to the airtight container 10 at the second fixing portion 38 , and the rotor of the motor 11 is included. 14 and the center of gravity G of the structure of the compression mechanism part 12 is located within the range of the distance H between the first fixing part 33 and the second fixing part 38 .

[fifth embodiment]

A fifth embodiment is disclosed in FIG. 14 . The structure of fixing the lower end part of the compression mechanism part 12 to the airtight container 10 of 5th Embodiment differs from 4th Embodiment.

As shown in FIG. 14, the 2nd cylinder 21b has the outer peripheral surface formed so that it may follow the inner peripheral surface of the container main body 10a. The second cylinder 21b is fitted inside the container main body 10a, and its outer peripheral surface is directly fixed to a predetermined position of the container main body 10a by welding or the like.

Therefore, in the fifth embodiment, the welding portion 91 formed between the third cylinder 21c and the container main body 10a constitutes the second fixing portion 38 for fixing the lower end portion of the compression mechanism portion 12 to the airtight container 10 .

Also in such a structure, the lower end portion of the compression mechanism portion 12 having the first to third refrigerant compression portions 15A, 15B, and 15C is fixed to the airtight container 10 at the second fixing portion 38 , and the rotor of the motor 11 is included. 14 and the center of gravity G of the structure of the compression mechanism part 12 is located within the range of the distance H between the first fixing part 33 and the second fixing part 38 .

Several embodiments of the present invention have been described above, but the above-mentioned embodiments are merely presented as examples and are not intended to limit the scope of the invention. The above-mentioned novel embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. The above-described embodiments and modifications thereof are included in the scope or gist of the invention, and are also included in the invention described in the claims and its equivalent scope.

Explanation of reference signs

2...rotary compressor, 4...outdoor heat exchanger, 5...expansion device, 6...indoor heat exchanger, 7...circulation circuit, 10...airtight container, 11...electric motor, 12...compression mechanism, 13...stator, 14 ...rotor, 15A...first refrigerant compression section, 15B...second refrigerant compression section, 15C...third refrigerant compression section, 16...first intermediate partition plate, 17...second intermediate partition plate, 18... 1st bearing, 19...2nd bearing, 20...rotating shaft, 33, 38...fixed part (1st fixed part, 2nd fixed part), 45...1st journal, 46...2nd journal, 48a ...1st crankshaft part, 47b...2nd crankshaft part, 47c...3rd crankshaft part, 48...1st intermediate shaft part, 49...2nd intermediate shaft part, G...center of gravity.

Claims (7)

1. A rotary compressor, having: Cylindrical airtight container; a compression mechanism section that compresses the refrigerant inside the airtight container; and an electric motor having: a stator fixed to the inner peripheral surface of the airtight container on the upper side of the compression mechanism part; and a rotor surrounded by the stator, and driving the compression mechanism part inside the airtight container, The above-mentioned compression mechanism unit has: a first bearing and a second bearing arranged at intervals in the axial direction of the airtight container; first to third refrigerant compression parts arranged at intervals in the axial direction of the airtight container between the first bearing and the second bearing; a first intermediate partition plate interposed between the first refrigerant compression unit and the second refrigerant compression unit; a second intermediate partition plate interposed between the second refrigerant compression unit and the third refrigerant compression unit; and The rotary shaft has: a first journal supported by the first bearing; a second journal supported by the second bearing; disposed between the first journal and the second journal, The first to third crankshaft parts that rotate eccentrically in the cylinder chambers of the first to third refrigerant compression parts and are fitted with roller sleeves; the first intermediate shaft located between the first crankshaft part and the second crankshaft part part; and a second intermediate shaft part located between the second crankshaft part and the third crankshaft part, the rotating shaft is fixed and rotated by the rotor of the electric motor, The compressing mechanism part is fixed to the airtight container by a pair of fixing parts provided at two places separated in the axial direction of the rotating shaft, and the center of gravity of the structure including the compressing mechanism part and the rotor of the electric motor is located in the airtight container. between a pair of fixed parts, The center of gravity is located on the axis of the first intermediate shaft portion. 2. The rotary compressor according to claim 1, wherein: One of the fixing parts is composed of a first supporting member fixed to the inner peripheral surface of the airtight container and connected to the first refrigerant compressing part closest to the electric motor, The other fixed portion is composed of a second support member fixed to the inner peripheral surface of the airtight container and coupled to the third refrigerant compressing portion farthest from the electric motor. 3. The rotary compressor according to claim 1, wherein: One of the fixing parts is composed of a first supporting member fixed to the inner peripheral surface of the airtight container and connected to the first refrigerant compressing part closest to the electric motor, The other side of the fixed part is constituted by a second support member sandwiched between the inner peripheral surface of the above-mentioned airtight container and the outer peripheral surface of the second bearing located at the lowermost part of the compression mechanism part, and the second support member is pressed into the inner peripheral surface of the airtight container and the outer peripheral surface of the second bearing. 4. The rotary compressor according to claim 1, wherein: One of the fixing parts is composed of a support member fixed to the inner peripheral surface of the airtight container and connected to the first refrigerant compressing part closest to the motor, The other fixed portion is constituted by a welded portion formed between the outer peripheral surface of the second refrigerant compressing portion and the airtight container, or between the third refrigerant compressing portion and the airtight container. 5. The rotary compressor according to claim 1, wherein: The first to third refrigerant compression parts of the compression mechanism part each have vanes that divide the cylinder chamber into a suction area and a compression area, Either one of the above-mentioned first intermediate partition plate and the above-mentioned second intermediate partition plate is composed of a pair of plate elements divided along the radial direction of the above-mentioned rotating shaft. a first concave portion of a bearing hole that supports the first intermediate shaft portion or the second intermediate shaft portion of the rotating shaft as a rotatable, Viewed in the axial direction of the rotating shaft, the joint surface of the plate element is provided at a position deviated from the range of 50° to 150° in the rotating direction of the rotating shaft with the direction of the blade as a reference point. 6. The rotary compressor according to claim 5, wherein: The above-mentioned joining surface of the above-mentioned plate element is constituted by a surface perpendicular to the axial direction of the above-mentioned rotating shaft, and a second recess is formed on the above-mentioned joining surface of the above-mentioned plate element, and when the above-mentioned joining surface is brought into contact with each other, the second recess A suction port for introducing refrigerant into the cylinder chamber is defined in cooperation with the suction port, and a connecting pipe is press-fitted into the suction port. 7. A refrigeration cycle device, comprising: a circulation circuit for circulating the refrigerant and connected to the radiator, expansion device and heat absorber; and The rotary compressor according to any one of claims 1 to 6 connected to the circulation circuit between the radiator and the heat absorber.

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